Clothes washing machine with control means for providing a varying speed tumble operation



March 9, 1965 c. w. BURKLAND 3,172,277

CLOTHES WASHING MACHINE WITH CONTROL MEANS FOR PROVIDING AVARYING SPEED TUMBLE OPERATION 2 Sheets-Sheet 1 Filed July 9, 1965 //vv/v7'0/? CHARLES W. BURK LAN D W AGE/v7 March 9, 1965 C. W. BURKLAND CLOTHES WASHING MACHINE WITH CONTROL MEANS FOR PROVIDING Filed July 9, 1963 A VARYING SPEED TUMBLE OPERATION 2 Sheets-Sheet 2 TIME CHARLES W- BURK LAND AGENT United States Patent Filed July 9, 1963, Ser. No. 293,771 1 Claim. (Cl. 68-12) This invention relates to washing machines and more specifically to a drive system for operating a substantially horizontal axis washer-drier combination at a plurality of speeds including a varying tumble speed, a distribution speed, and an extraction speed using a two-speed motor and a two-speed transmission.

It is well-known in the art to provide a horizontal axis washer or a combination washer-drier with three speeds of operation for achieving the most satisfactory laundry results. In addition, ithas been found that to achieve proper washing action for all types of clothes loads, a variable tumble speed is desirable.

I have found that by pulsing or cycling the motor between two predetermined speeds of operation with proper intermediate time delays that a tumble speed varying between a distribution speed and a below normal tumble speed resulting in a desirable washing action may be obtained. This Washing action gives improved cleaning results for a wide range of sizes and types of clothes loads. In addition, if the pulsing is accomplished rapidly, a substantially constant third speed may be achieved.

It is therefore an object of this invention to provide for a horizontal axis washing machine, a drive system in which a tumble operation is obtained by pulsing or cycling the motor between two sets of windings.

It is another object of this invention to provide a drive system for a horizontal axis washing machine in which a varying speed tumble operation is obtained by alternately energizing and de-energizing two sets of run windings of a two-speed drive motor.

It is a further object of this invention to provide a drive system for a horizontal axis washing machine in which the clothes container is rotated at distribution and at extraction speeds by a conventional electric motor and twospeed transmission means and in which a varying speed tumble operation is obtained by pulsing or cycling between the four-pole and six-pole windings of a two-speed motor at predetermined time intervals.

Further objects of the invention will become evident as the description proceeds and from an examination of the accompanying drawings which illustrate a preferred embodiment of the invention and in which similar numerals refer to similar parts throughout the several views.

In the drawings:

FIGURE 1 is a rear elevational view partially in section of a combination washer-drier unit embodying the drive system of the present invention;

FIGURE 2 is a side elevational view partially in section of the combination washer-drier unit of FIGURE 1 and more specifically showing the motor and two-speed transmission;

FIGURE 3 is an electrical schematic circuit showing the electrical connections to the drive system and controls related thereto; and

FIGURE 4 is a typical speed curve of the combination washer-drier during the portion of the cycle in which the motor is pulsed or cycled.

Referring now to the accompanying drawings in detail, it will be seen that the combination washer-drier unit embodying the present invention and shown in these drawings includes a substantially flat surfaced base frame mounted on legs 11. Mounted upon base frame 10 3,172,277 Patented Mar. 9, 1965 are the channel members 13 and 14 which are welded or securely affixed in some suitable manner to the base frame 10 to form the two major supports for the washerdrier unit illustrated in the accompanying figures.

As seen in FIGURES 1 and 2, channel members 13 and 14 are substantially triangular in elevational configuration with the apex of these members receiving pivot pins 16 and 17. These pivot pins 16 and 17 support tub brackets 21 and 22 to provide a two-point support for the tub or casing which is generally indicated by the arrow 24. Tub 24 which is fastened to brackets 21 and 22 may thus oscillate back and forth on pins 16 and 17 in an arcuate movement in response to various forces generated within that tub.

Tub 24 is maintained in an upright position on pins 16 and 17 by two centering springs 25 connected between tub 24 and base 10 through the spring connector brackets 26 fastened to the latter member. FIGURE 1 shows the tub 24 as being provided with a tub damper bracket 28 which forms the support for the damper leaf spring 29 carrying the damper pad 31 in a ball and socket joint at the end of damper leaf spring 29. Base frame 10 is provided with an upstanding damper plate 32 which is engaged by the damper pad 31 to absorb and dissipate the energy imparted to tub 24 causing it to oscillate on the supporting pins 16 and 17.

Tub or casing 24 includes a generally cylindrical side wall 71, a pair of spaced rear walls 72 and 73 and a front wall 74. The front and outer rear walls 74 and 72, respectively, are connected to cylindrical side wall '71 by means of the encompassing flanged hoop-like members 76 while the partition wall 73 positioned between walls 72 and 74 is welded to side wall 71. It will be seen from an inspection of FIGURE 2 that the spaced rear walls 72 and 73 support the tub bearing assembly generally indicated by the reference numeral 80.

The tub bearing assembly 80 includes a spacer hub 81 which is located between and which abuts the rear walls 72 and 73, and a tubular clamp member 82 located concentrically within hub 81. Clamp member 82 is formed with a shoulder 85 and has a threaded portion 84 for receiving spanner clamp nut 83 which, when tightened on member 82, produces a rigid support with respect to tub 24 for two bearings (not shown) one of which is located adjacent each of walls 72 and 73 for support of drum drive shaft 89.

The rear end of the drum drive shaft 89 is rigidly connected to the large drive pulley 91 whereas its front end is threaded into hub 94 of the drum or clothes receptacle 95. Drum 95 includes a perforate rear wall 96 which is rigidly affixed to and cooperates with the spider-like member 97 to form a double cone support connected to the hub 94 and providing a rigid support for the clothes basket 95 on drum drive shaft 89. A sealing member 101 is biased against the rear surface of this revolvable hub structure 94 to prevent water from the tub 24 from entering tub bearing assembly 80.

' As apparent from FIGURE 2, the clothes drum 95 also includes a perforate cylindrical side wall 104 carrying clothes elevating vanes 105. Side wall 104 merges into the short front wall 106 and joins the flanged rear wall 96 in an overlapping relationship to form a protruding flange 108 which, while not touching wall 73, cooperates with that wall 73 to form an elfective air seal to prevent heated air entering tub 24 through cylindrical side wall 71 during the drying operations from being short circuited around the rear peripheral edge of drum 95.

Tub 24 is connected at its lower portion with a drain pump 112 which communicates with an external drain for removing fluids from tub 24.

Tub 24 also includes the circular loading opening 117 which is encircled by the bellows seal 118 having its opposite end fastened to a similar opening formed in the cabinet 119 enclosing this combination unit. Sealing member 118 includes a number of convolutions 121) permitting, arcuate movement of tub 24 relative tocabinet .119. A rectangular door 121 hinged on cabinet 119 carries a transparent;glassdoor 122 having a cylindrical.- portion extending rearwar dly through the bellows seal 118 which is provided with a flexible annular sealing lip 124 engageable with the periphery of. the glass door 122. This seals. the unit while enabling the. operator of the machine to observe operations taking place within tub 24. during the washing and drying processes. The, lamp126v fastened to the exterior of tub. 24 shines through a transparent member 127 carried-in tub 24 for illuminating the interior of.the machine during the loading operations.

' Tub 24 also includes aheater housing. .131 which may be formed separately or as a part of the casing side wall and which supports a heatingelement (notshown) capable, of. radiating heat energy through an opening.

located in thecylindrical tub wall 71 and covered by the heater. housing 131. Heater housing 131: also mounts thethe thermostat133. which is connected in series withthe heater.

The power to rotate drum 95 through the large pulley 9 1 is applied by the two-speed motor 137. mounted on bracket 138 carriedon a lower portion of tub 24. Twospeed motor 137 is operable at a speed. of approximately 1725 revolutions per minute when its four-pole run windings 135 are energized and operable at a speedgof approximately 1150 revolutions per minute when its sixpole run windings136 are energized. The output shaft of motor 137' is connected to a flexible. universal coupling 139 which is connected in turn to the. transmission input shaft 140 constituting an extension of the motor shaft.

A split pulley 141 having. a pair of axially separable.

mission unit 145 and the pulley 146afiixed to the end of that portion of; shaft140extencling completely through transmission 145. Transmission 145 is provided withan output pulley 147 which is connected to the large drum shaft pulley 91. through belt 148.

With motor 137 operating at a speed of 1725 revolutions per minute, an. energization of solenoid 149, which controlstheoutput speed of transmission 145 and thus the speedy of pulley .147, causes the clothes receptacle 95. to berotated at a speed of approximately 300 revolutions per minute while de-energization of. that solenoid returns transmission. 145 to. the condition of maximum speed reduction for driving receptacle 95 at a speed of approximately 60 revolutions per minute.

Thepulley. 146 affixed to the end of shaft 1481s connected to the fan pulley 151. through the belt -2 so.

as to drive the pulley 151 at a speed approximately equal to that of motor 137;

A combination transmission support and belt tensioningdeviceis provided by the slotted bracket 158 which is. connected to the rear, wall 72 through the adjustable machines'crews 159.

fan. pulley 151 and the slack taken out: of belt 152. The slack is automatically taken out of the tumbler drive.

Bracket 158 journals shaft. 148 allowing transmission unit 145 to pivot freely aroundbelt 148 by means of the compression spring 161 mounted between bracket 158 and the transmission unit and tending to pivot the transmission 145 downwardly around shaft 140. The tension in the drain pump belt 144 is automatically maintained during these adjustments by means of the spring biased split pulley 141.

A conventional unbalance control system (notshown) may be provided for controlling operation of the machine during the extraction operation to eliminate the possibility of walking of the machine or damage thereto resulting from forces that may be generated'by the unbalanced spinning container.

A combination blower-condenser unit capable of moving air through tub 24,, scrubbing lint and condensing out moisture from hot vapors produced within casing 24 during its drying operations, is positioned in the compartment formed by and between the portions of the spaced walls 72, and 73.

The compartment for the blower-condenser unit is produced by the cooperation of Walls 72 and 73.with an imperforate scroll-shaped side. wall 166 shown by dotted lines in FIGURE 1 Which'bridges the space between walls 72 and 73 to enclose the. vapor condenser andblower unit. Water isv directed towards an impeller (not shown) and the actionof the rotating impeller upon" the. stream of water produces a cool mistspray and fog for condensing out hot moisture vaporsentering the blower, condenser unit during. the drying. operation of this combination machine.

An impeller (not shown) positioned behind plate 163 is driven by blower pulley 151. Plate 163. is bolted to'the rear wall 72 of tub 24 and provides access to the blower housing.

The water for the vapor condensing operation is suppliedthrough the external conduit 172 and is directed into the condenser unit by conduit 171. Water for the washing operation is supplied throughthe conduit 173' which empties'into cup. 174 provided with a flapper check valve 175.and' draining intotub 24 between walls73 and 74; Flapper valve 175' not only prevents suds'from escaping from tub 174 during thewashing operation but also preventslsteamy vapors from escaping fromthe washing and drying chamberof tub 24 and condensing on the cooler interior surfaces of cabinet 119.

As previously indicated, it is well-known within the laundry appliance industry to provide three speeds of operation of the clothes receptacle in horizontal axis washing machines. and in washer-drier combination units. These three receptacle speeds' or velocities include a tumble speed for accomplishing the washing action, a low extraction, or distribution, speed for allowing the fabrics to arrange. themselves in a substantially 'even pattern around the inner periphery of the washing receptacle or container and becoming plastered thereto and a third relatively high speed for accomplishing fluid extraction.

As previously shown, motor 137 and transmission 145.

the two sets of run windings under control of a timing;

device. Referring to: FIGURE 3, an electrical schematic diagram shows thecomponents and circuitry of one em: bodiment for achieving the desired cycling.

Provided across power lines L and L is conventional 110 volt 60 cycle alternating current-for operating the- Included in the electrical-circuit of.

electrical devices. FIGURE 3 is the start winding 1800f conventional twospeed'motor 137 in series connection. with starticapacitor 181. Start winding is connected .acrosspower lines L and L in a parallel relationship to four-pole run windduring a washing or drying operationis obtained;

ing 135 and six-pole run winding 136. In series with start winding 180 is the centrifugal switch 183 for interrupting current to start winding 131) at a predetermined motor speed. Centrifugal switch 183 is mechanically linked with switch 184 for operating switch 184 from contact 185 to contact 186 upon opening of centrifugal switch 183. Switch 184 is made to contact 185 during periods of energization of start winding 189 for insuring energization of four-pole run winding 135 during the starting operation.

Controlling energization of run windings 135 and 136 is pulsing or cycling switch 189 which is operable in a first position for completing a circuit to six-pole run Winding 136 through contact 191 and operable into a second position for completing a circuit to four-pole run winding 135 through contact 190. Switch member 189 is biased in a direction for closing to contact 191 and is actuated to the position of closing to contact 191) by cam member 194.

Cam member 194 is provided with rises or lifts and is driven by motor 195 at a relatively slow timing speed for operating switch 189 at predetermined time intervals. Energization of motor 195 is controlled by contact members 197, 198, and 199 of a conventional sequence timing mechanism (not shown).

Also forming a part of the sequence timing mechanism are contacts 202 and 203 for controlling energization of spin solenoid 149. Upon the closing of contact members 202 and 293, spin solenoid 149 is energized for shifting transmission means 145 to a condition for driving container means 95 at fluid extraction speeds.

Thus during selected portions of the cycle of operations, such as during tumble operations, timer contact 197 may be closed to contact 193 for energizing motor 195. When motor 195 is energized, cam member 194 is driven at a slow timing speed for cycling switch 189 between a position for completing a circuit to contact 191 and a position for completing a circuit to contact 190. Motor 195 may be operable at three revolutions per minute, for example, for driving cam 194. As previously indicated, cam 194 is provided with operating means so spaced as to operate switch 189 between contact 191 and contact 190 for providing predetermined time intervals in each of the two positions. The operating means on cam 194 may, for example, allow switch 189 to make to contact 191 for three seconds and then actuate switch 189 to contact 191) for a period of two seconds for providing three seconds of operation at the six-pole energization and two seconds of operation at four-pole energization. Thus, when earn 194 is driven by a three revolutions per minute motor (20 seconds per revolution), the above five second switching cycle would be repeated four times per revolution.

Operation of this invention for providing the desired three speeds of operation including a variable tumble speed is best understood by considering operation of the motor and transmission through a full cycle of operations. Upon initial energization of the machine for the first tumble portion of the cycle, contact 197 is closed to contact 198 for energizing pulsing motor 195. Coincident with closing of contacts 197, 198, starting winding 18% is energized through centrifugal switch 183 closed to contact 182. Upon energization, motor 195 drives carn 194 for alternately closing switch 189 to contacts 190 and 191. Since switch 184 is closed to contact 185 during the starting operation, four-pole run winding 135 will be energized during that period regardless of the position of switch 189. Thus, with energization of run winding 135 and start winding 189, motor 137 will'be accelerated at a rate dependent upon variables including voltage across lines L and L and size of the load carried by container 95. At a given speed of operation, centrifugal switch 183 will open to de-energize run winding 180 and to close switch 184 to contact 186.

Upon closing of switch 184 to contact 186, six-pole run winding 136 becomes energizable upon closing of switch 189 to contact 191. Throughout the tumble operation, pulsing motor 195 remains energized for cycling switch 139 between contacts 190 and 191 at predetermined time intervals for alternately energizing four-pole winding 135 and six-pole run winding 136. Energization of run winding 135 for a period of approximately two sec onds will allow motor 137 to accelerate under normal operating conditions to its higher operating speed of 1725 revolutions per minute and allow operation at that speed for a period of time. This motor speed corresponds to a container speed of approximately 60 revolutions per minute when solenoid 149 is de-energized. Upon move ment of switch 189 to contact 191 and energization of six-pole run winding 136, motor 137 will decelerate under the loading of basket and material contained therein. Since switch 189 is made to contact 191 for approximately three seconds, the deceleration continues until the motor is operating at the six-pole operating speed of approximately 1150 revolutions per minute. The three second period of time is normally suficient to allow the motor to operate at this lower speed for a period of time for driving basket 95 at a below normal tumble speed of approximately 40 revolutions per minute.

Thus it is seen that the cycling of switch 189 provided by motor 195 and cam 194 will alternately energize fourpole run winding and six-pole run winding 136 at predetermined time intervals for operating motor 137 within a speed range varying between the normal sixpole and four-pole speeds for driving basket 95 at tumble speeds varying between a slow below normal tumble speed and a distribution speed.

Referring briefly now to FIGURE 4, there is shown a typical or representative speed curve for the container or receptacle during the tumble operation. This speed curve includes a period of acceleration I to the higher motor speed, a period of operation at that upper motor speed 11, a period of deceleration III from the upper speed to the lower speed, and a period of operation at the lower motor speed IV.

Upon completion of the washing portion, the machine Will proceed through a series of rinses during which the container 95 will continue at tumble speeds.

Following completion of the series of rinses, the machine is energized under control of the timer mechanism for proceeding through the fluid extraction portion of the series of operations. At this time, timer contacts 197, 198 are opened and contacts 198, 199 are closed. As previously indicated, the high speed fluid extraction operation is proceeded by an operation for distributing the materials about the inner periphery of the basket 95. This distribution speed is accomplished with motor 137 energized for its upper output speed and transmission operating in the condition of maximum speed reduction with solenoid 149 de-energized. Motor 137 is operable at its upper speed when energized through its fourpole run winding 135 in series with switch 189 made to contact 190.

Because of the cycling of switch 189, it is possible for this switch to be made to contact 191 at that time at which it is desired to energize four-pole run winding 135 to obtain the upper motor speed for driving the container at distribution velocity. If switch 189 is made to contact 191 at the beginning of the distribution operation, a circuit is completed between power lines L and L through switch 1189, contact 191, line 212, timer contacts 199, 198 to pulsing motor 195 for advancing cam 194. Upon energization of motor 195, cam 194 is advanced to a position at which switch 189 is actuated from contact 191 to contact 191 for de-energizing the pulsing motor 195 and energizing four-pole run winding 135.

With switch 189 made to contact and timing motor tie-energized, motor 137 is energized in a steady condition for providing a distribution speed of approximately 60 revolutions per minute as shown by portion V of speed curve of FIGURE 4.

Following completion of the desired distribution operation, container'QS is driven rat fluid extraction speeds upon speed and with'the.highspeedsolenoid energized.

The fluid extractionoperation may also, of course, be followed by an additional tumbling operation, as in a combination washer-drier, With heat on for drying the fabrics;

Referring again to FIGURE 4, it is noted that the typical: or representative speed curve as shown includes an alternating series of accelerations and substantially constant speed operations. The periods of constant speed represent operation 'of'the motor at its two designed operating-speeds and are connected by speed curves representing an acceleration, either'positive or negative, of the motor or container. The portions of the speed curve shown'as I represent positive acceleration of the motor when energized: across its four-pole winding for the upper operating speed. The periods of negative acceleration, or deceleration, represented by III, are the result of the combined effects of energizing the motor while operating at its upper speed for operation at its lower speed and'the loading of the container and materials contained therein.

The general shape of the speed curve shown in FIG- URE 4 is determined by the rate of cycling of switch 189. Point A represents the moment at which switch 189 is made to contactliil for energizing the motor for operation at its lower speed. The motor thus decelerates to its-lower speed-along a path indicated by III and then continues to'operate at a substantially constant speed as indicated by the portion IV. At point B, switch 189.

is actuated to-contact 1%. for energizing four-pole run winding 135- for: accelerating motor 137 to its upper speed. Motor 137', and thus container 95' also, is accelerated to the upper, or distribution speed, at which container95' is rotated for a period of time. The elapsed time between Aand B is thus the time of energization of six-pole run winding 136: and is determined by control cam 194 as drivenby motor 195. The elapsed time between point B and point A'is that period of energization: offour-pole run'windingv 135 and is likewise determined by control cam 194.

It is noted that the. relative lengths of time each run windingis energized may be altered to provide a some- What different speed'curve and resulting container speed. By reducing the elapsed time, for example, between point A, B, and between B, A, the motor may bemore rapidly cycled for controlling motor operation to a relatively constant speed.

It is also noted that unusual operating conditions may alter the. typical speed curve of FIGURE 4. Low voltageconditions, for example, will result in a slower'acceleration anda shorter'period of time for. operation at theupper speed or plateau indicated by H. In addition,

unusually heavy loads within container 95 will cause fastcr'deceleration. from point A and will result in a longer period ofoperation at the lowermotorspeed.

It is thus seen that the present invention provides a drive system for a horizontal axis washing machine or combination washer-drier inwhich a varying tumble operation is obtained by pulsing or cycling the motor between two sets of run windings. This varying tumble operation is both advantageous in providing a more desirable washing action'and in providing a more desirable tumble dry operation.

In the drawings and specification, there has been set forth-a preferred embodiment of the invention and, although specific terms are employed, these are used in a generic and descriptive sense only, and not for purposes of limitation. Changes in form and proportion of'parts', as well as the-substitution of equivalents, are contemplated as circumst'ances-may suggest or-render expedient, without departing from the spirit or scope of this invention as further defined in the following claim.

I claim:

in a laundry machine operable through a series of operations including tumble, distribution, and extraction operations and having container means rotatable about a non-vertical axis for receiving. materials to be washed therein, the combination comprising: a primary timing.

device for controlling said laundry machine through said series of operations; electric drive motor means having a first run winding and a second run winding individually energizable for selective operation of said motor at a first-speed'and at a second'higher speed; first circuit means having switch means operative in a first position for energizing said first run windingand operative in a second position 'for energizing said second run winding; second circuit means including an auxiliary timing motor means; cammeans driven by said auxiliary timin'gmotor means controlling said switch means for alternately energizing said first and second run windings for predetermined-intervals of time for acceleration to said second speed and for deceleration from saidsecond speed to said:

first speed at predetermined time intervals, said primary timing device being operative for limiting said auxiliary timing motor means 'to operation during. said tumble operation; transmission means operable in a first condition to drive said container at 21' below normal tumble velocity and actuatable to a second condition to drive said container at'a first extraction velocitywith said drive motor means operatingat said first speed, said trans mission means being further operable in said first con-- dition to drive said container means at a distribution. velocity and actuatable to saidsecond condition to drive said container means at a second higher extraction velocity with said drive motor means operating at said second speed, said drive motor means and said transmission meansbeing cooperable and responsive to the al-' ternating 'energizationof said first and said secondrun windings for driving-said container means at velocities varying between said below normal-tumble velocity andsaid distribution velocity to tumble materials containedtherein.

References tjited bythe Examiner UNITED STATES PATENTS 1,477,862 12/23 Barr 318 -164 2,06(),43-7 11/36 Harley 318-164 2,556,490 6/51 Chamberlin' 68-24 X; 2,881,633 4/59 Warhus 68- 24 X 3,003,091 10/61" Shewmon et al. 3l8'224.1 X 3,055,203 9/62 Toma 6824 X WALTER A. SCHEEL, Primary Examiner. WILLIAPVI I. PRICE, Examiner. 

